Two mass swing system with independently controlled vibratory exciter means

ABSTRACT

A tuned two mass swing system including a base reaction mass and a frame feeder mass supported thereon by elastic coupling means permitting independent horizontal and vertical natural frequencies and independent horizontal and vertical components of vibration effective to swing the feeder frame in a controlled excursionary vibratory path for feeding material. An independent horizontal vibratory exciter means and an independent vertical vibratory exciter means is required to supply the independent horizontal and vertical components of vibration. Through a control means connected to independently and variably control the exciter means enables one to adjust the magnitude of each of the horizontal and vertical components of vibration and also to independently and variably adjust the operating phase relationship between the horizontal and vertical components of vibration for the purpose of regulating the action of the material moved. This is true of a straight feeder as well as a bowl feeder. One set of flat leaf springs disposed in the horizontal plane and with their adjacent ends connected to another set of flat leaf springs disposed vertically may be employed as the elastic coupling to provide the independent horizontal and vertical natural frequencies and the independent motion resulting in the vertical and horizontal components respectively. This may also be obtained through the use of resilient material fastened on the one side to the reaction base and on the other side to the feeder frame. A single or a multiple number of elastic members may be employed to support the feeder frame when independent horizontal and vertical components are applied thereto. Thus the structure of the elastic support together with the control enables one to independently regulate the action of the material moved by the feeder means.

Dec. 9, 1975 United States Patent Brown effective to swing the feederframe in a controlled excursionary vibratory path for feeding material.An independent horizontal vibratory exciter means and an independentvertical vibratory exciter means is re- 1 TWO MASS SWING SYSTEM WITHINDEPENDENTLY CONTROLLED VIBR ATORY EXCITER MEANS [75] Inventor: wllhamBrown Blalrsvlue quired to supply the independent horizontal and verti-[73] Assignee; FMC Corporation, San Jose, Calif. cal components ofvibration. Through a control means connected to independently andvariably control the [22] Flled' Sept 1966 exciter means enables one toadjust the magnitude of [21] Appl. No.: 581,058 each of the horizontaland vertical components of vibration and also to independently andvariably adjust the operating phase relationship between the horizond tip p y f vibration for th pur- [58] Fie'id pose of regulating the actionof the material moved. This is true of a straight feeder as well as abowl feeder. One set of flat leaf s rin s dis osed in the hori- [56]References cued zontal plane and with their dja ent e iids connected toUNITED STATES PATENTS another set of flat leaf springs disposedvertically may 2,629,485 2/ 1953 Sherwen 198/220 be employed as theelastic coupling to provide the in- 2,746,599 5/1956 Weyandt.... 198/220dependent horizontal and vertical natural frequencies 3,203,264 8/1965Evans I98/220 and the independent motion resulting in the vertical3,315,793 4/1967 Yakubovich 198/220 and horizontal componentsrespectively i may also be obtained through the use of resilientmaterial fastened on the one side to the reaction base and on the otherside to the feeder frame. A single or a multiple number of elasticmembers may be employed to support the feeder frame when independenthorizontal and vertical components are applied thereto. Thus the PrimaryExaminerE. C. Blunk Assistant Examiner.l. V. Nase Attorney, Agent, orFirm.lohn R. Swindler [57] ABSTRACT A tuned two mass swing systemincluding a base reaction mass and a frame feeder mass supported thereonby elastic coupling means permitting independent horizontal and verticalnatural frequencies and independent horizontal and vertical componentsof vibration structure of the elastic support together with the controlenables one to independently regulate the action of the material movedby the feeder means.

30 Claims, 14 Drawing Figures U.S. Patent Dec. 9, 1975 Sheet 1 of 63,924,730

US. Patent Dec. 9, 1975 Sheet 2 of6 3,924,730

U.S. Patent Dec. 9, 1975 Sheet 4 of6 3,924,730

U.S. Patent Dec. 9, 1975 Sheet 6 of6 3,924,730

TWO MASS SWING SYSTEM WITH INDEPENDENTLY CONTROLLED VIBRATORY EXCITERMEANS This invention relates generally to a two mass swing systemcoupled by elastic means commonly employed as a material handling deviceand more particularly to the apparatus and method for variableadjustment of the vibratory components of force imposed upon the systemto effect -a change in the magnitude of the vibratory components offorce and in the phase relation between such vibratory components offorce to produce a change in the excursionary path of displacement andobtain optimum feeding action for any given feeding application.

The art of vibratory feeding devices is a well established art whereingenerally a two mass system is coupled together with an elastic meanssuch as leaf springs and set into vibratory motion with a vibratoryexciter means, such as, an eccentric weight motor or electromagneticmotor mounted on one of the masses. In the latter case, a coil-woundcore is secured to one mass and its armature on the other mass, so that,upon energizing the coil from an alternating or pulsating source,self-induced vibratory modes of motion are imposed upon the system.

With a given two mass system, the angle of resultant vibratory motion orfeed angle of the system remains the same. This presents a problem incommon practical application of such vibratory material handlingdevices, in that, a two mass swing system constructed for a particularfeeding application is not necessarily useful in another feedingapplication due to differences in the materials to be handled includingsuch considerations as the size, weight, coefficient of friction, etc.Thus particular attention is always directed to the feed angle to bedesigned into the system depending upon the particular feedingapplication. In order to apply the same ma terial handling device toanother feeding application, the feed angle of the entire system may,necessarily, therefore have to be changed. The most expedient andsimplest method to vary the feed angle is to change the elastic orspring means specifications. Such a change would not only be timeconsuming and bring about additional expense for each change of the feedangle of the system but also limits the productive use and overallutility of such material handling devices.

The principal object of this invention is the provision of a universaltwo mass swing system which may be adjusted to provide optimum feedingrequirements for a broad range of load conditions and feedingapplications without changing or interfering with the naturalfrequencies of the system.

Attempts have been made in the past to provide such a universal two massswing system but these applications always involved a simultaneousadjustment in or interfere with the natural frequency of the system.Such examples are illustrated by US. Pat. Nos. 3,048,260 and 3,258,1 ll.In such systems as taught in these patents, the swing motor systemincorporates an adjustable means to permit a change in the angle ofresultant vibratory motion imposed upon the system in order tocompensate for variable load conditions. In each of these systems theadjustment made to provide for an optimum feed rate also simultaneouslyeffects the natural frequency of the system requiring additionaladjustment in natural frequency. The practicality of such ad- 2justments becomes impermissible in material feeding applicationsinvolving a broad range of variable load conditions.

Another object comprising this invention is the provision of a flexible,readily adaptable two mass swing system having versatile control of thevibratory components of motion imposed upon the system and thus capableof providing optimum feeding requirements over a wide range of variableload conditions eliminating inherent problems present in the prior art,such as, retuning of the whole two mass swing system, narrow limits ofoptimum feed adjustment present in such systems and the time required toaccomplish the retuning of the system.

Another object comp rising this invention is the provision ofindependently controlled vibratory exciter means in a two mass swingsystem which are independently controlled to change the phase relationof one relative to the other to produce various paths or wave shapes ofmotion on the masses of the system and, thus, provide variable controlof the rate of feed of material to obtain the optimum feed rate for awide range of feeding applications.

An important improvement residing in the structure comprising thisinvention over the prior art in ease and ability to adjust the two massswing system for optimum feeding without making a mechanical adjustmentin the two mass system, the latter which will effect the naturalfrequencies of the system. Rather, the operating phase relation betweenthe exciter means is controlled in order to obtain optimum feed ratesfor a range of variable feeding applications without interfering with oreffecting the natural frequencies of the entire two mass system.

In any two mass vibratory system, the natural frequency in onepermissible plane of movement should be substantially the same as thatin the other permissible plane of movement. In the feeding applicationof a two mass torsional swing system, the natural frequency in thevertical mode of permissible movement should be substantially the sameas that in the torsional mode. In this particular vibratory system, inorder to obtain the desired natural frequency of these modes, the loadand mass in the vertical mode to be set into vibratory motion must betaken into consideration, while in the torsional plane, the moments ofinertia must be considered in order to properly determine the properspecifications of the elastic coupling means. A principal featurecomprising this invention is a control means, divorced from themechanical aspects of the two mass system, eliminating constantconsideration of the selection of elastic coupling means in themanufacture of a material handling device to obtain the desiredfrequency of the modes of vibration for each given set of loadconditions.

Another object comp rising this invention is the provision of elasticcoupling means which permit independent directional modes of vibrationupon excitation, which, when independently controlled, permit a widerange of control of the path of motion of the feeder frame of thematerial handling device. The frequency of excitation imposed upon eachmode of vibration can be independently adjusted to obtain various formsof the combined pattern of movement, such as an elliptical path ofvariable eccentricity. Such an elastic coupling means permitsflexibility in the selection of the natural frequency of each mode ofvibration as well as the exciting frequency.

Another object comprising this invention is the provision of a controlmeans to permit adjustment of the operating phase relation which is thesequence of the imposed modes of vibratory motion induced in the twomass swing system by the vibratory exciter means. Each of the excitermotor means is independently controlled through a circuit in order tochange the phase relation between the horizontal mode of motion producedby one of the exciter means and the vertical mode of motion produced bythe other of the exciter means in order to arrive at the desired imposedexcursionary path of motion imposed on the feeder frame.

Another object comprising this invention is the provision of a phasecontrol to compensate for the adverse effects of dampening caused by theintroduction of load into the material handling device. This dampeningeffect causes a phase shift between the separate modes of vibration, inthat, the period of vibration of the vertical mode of vibration is notin proper time sequence with the horizontal mode of vibration.Adjustment may be made with the control means impedance of the verticalmode of vibration to bring these component modes of vibration back intoa proper phase relationship.

A circuit is supplied to control the excitation of the exciter means aswell as vary the operating phase relationship between the horizontal andvertical components of vibration. The phase relationship may be definedas the phase sequence between the horizontal mode of motion and thevertical mode of motion. The change in phase relation is produced bychanging the operating phase relationship between the applied voltageand current to one of said exciter means. An important object comprisingthis invention is the provision of an elastic means which permits twodifferent directional modes of vibration, the resultant effect of themodes being imposed upon the feeder frame of the material handlingdevice. The ability to control the different directional modes ofvibration permits optimum control over the resultant vibratory patternof motion imposed upon the feeder frame.

Another important object comprising this invention is the provision ofelastic coupling means consisting of an annular elastomer. The use ofthis elastomer in the two mass swing system permits flexibility in thesystem relative to the induced vertical and horizontal modes of motion.Also the employment of an elastomer coupling means permits the completesealing of the interior of the vibratory material handling device fromdust and other foreign matter.

Another object comprising this invention is the provision of elasticcoupling means in a two mass swing system consisting of jointed andsymmetrically balanced horizontally and vertically disposed sets ofparallel leaf springs in planes normal to one another and connected atone end to one of the masses and at the other end to the other of saidmasses.

Another object comprising this invention is the provision of elasticcoupling means in a two mass swing system consisting of a series ofelastic springs capable of flexing either horizontally or vertically andsecured at one end to one of the masses and at the other end to theother of said masses.

Another object comprising this invention is the provision ofindependently controlled horizontal and vertical vibratory exciter meanswhich includes a phase relation control means and amplitude controlmeans to selectively vary the vibratory action of each of the excitermeans independently of the other to effect a full range of obtainableselective vibratory components of motion, the combined effect whichproduces a resultant vibratory motion on the masses in the two massswing system.

Another object comprising this invention is the method of varying thephase relation of the vertical and horizontal components of vibratoryforces in a vibratory material handling device without effecting thevertical and horizontal natural frequencies of the material handlingdevice to select the optimum feed rate for a given feeding application.

Another object comp rising this invention is the provision of the methodof varying the direction of movement of material being fed and conveyedby a vibratory material handling device without effecting the desirednatural frequencies of the vibratory handling device as well as thepreselected optimum feed rate imposed thereon.

Another object comprising this invention is the provision of a method ofvarying the operating phase relation of vertical and horizontal feedingcomponents of vibratory forces imposed on a feeder mass in a materialhandling device without affecting the natural frequencies of the deviceby adjusting the phase relation of the amplitude of vibration of aselected vibratory component relative to the other vibratory componentwhile simultaneously adjusting the magnitude of one vibratory componentrelative to the other to obtain the optimum material feed rate imposedupon the material being moved for any given feeding application.

Another object comprising this invention is the provision of a method ofcontrolling the path of movement of materials being moved in a materialhandling device without affecting the natural frequencies of the deviceby selectively adjusting the phase relation between the horizontal andvertical vibratory feeding components imposed upon the device by thevibratory exciter means to change the excursionary path of displacementof the feeder frame.

Other objects and advantages appear hereinafter in the followingdescription and claims.

The accompanying drawings show for the purpose of exemplificationwithout limiting the claims thereto, certain practical embodimentswherein:

FIG. 1 is a view in side elevation of a material handling device withparts of the housing in section.

FIG. 2 is a plan view of the material handling device of FIG. 1 withparts of the frame in section.

FIG. 3 is a sectional view in side elevation showing a modified form ofthe material handling device of FIG. 1.

FIG. 4 is a proportional view and side elevation of a material handlingdevice showing a further modification of the material handling device ofFIG. 1.

FIG. 5 is a sectional view in side elevation of a material handlingdevice illustrating a novel spring structure.

FIG. 6 is a plan view of the material handling device of FIG. 5 withparts of the frame in section.

FIG. 7 is a proportional sectional view of a material handling deviceemploying a modified elastic coupling means as compared to thatillustrated in FIG. 5.

FIG. 8 illustrates a further type of elastic means for the materialhandling device of FIG. 5.

FIG. 9 is a view in side elevation of the material handling deviceshowing wire spring inserts with parts of the housing in section.

FIG. is a plan view of the material handling device of FIG. 9 with partsof the frame in section.

FIG. 11 is a view in side elevation of the material handling device ofstraight feeding design employing the elastic coupling means of FIG. 5with parts of the frame in section.

FIG. 12 is a sectional view taken along the line l2-12 of FIG. 11.

FIG. 13 is a sectional view of a material handling device of straightfeeding design employing the elastic coupling means of the materialhandling device of FIGS. 1 through 3.

FIG. 14 shows the electrical circuit diagram for controlling theoperation of the material handling devices of FIGS. 1 through 13.

FIG. is a schematic circuit diagram for controlling the operation of thehorizontal and vertical motors.

Referring now to the drawings showing a two mass swing system comprisingthis invention and more particularly to FIGS. 1 through 4, the two massswing system consists of a base 1 supported on isolators 2 with a framemass 3 to which horizontal and vertical components of vibration areimparted to a feeder bowl 4, illustrated in part in the figure. Thefeeder bowl 4 and the frame mass 3 are coupled to the base mass by anelastic coupling means generally illustrated at 5.

As well known in the vibratory art, the base mass 1 is made preferablemore massive by the addition of weight so that in the operation of thetwo mass swing system the rotational inertia of the base mass 1 is muchlarger than that of the feeder mass 3 and its accompanying feeder bowl4. Vibratory exciter means, such as the several types illustrated in US.Pat No. 3,258,11 1, are employed to impart the necessary components ofvibration to the frame mass 3 through the elastic coupling means 5. Asshown in FIGS. 1 through 4, the vibratory system is set into motion bythe electromagnets 6, 7 and 8.

It will be noted that everything connected with the frame mass 3constitutes a specific mass, which, when coupled to the base 1, resultsin a combined inertia mass system having a specific vertical naturalfrequency and specific torsional natural frequency of vibrationdepending on the material characteristics of the elastic coupling means5.

The base mass 1 comprises the annular support member 10, which issecured to the housing 1 1 utilizing the fastening bolts 19. The annularsupport member 10, as shown in FIG. 1, supports the elastic couplingmeans 5 which consists of the elastomer 12 secured between the annularelastomer support members 13 and 14. The elastomer support member 13 issupported by the annular support member 10 of the base mass 1. The innerelastic support ring 14 is secured to the cylindrical housing 15 whichis part of the frame mass 3.

The upper elastic coupling means 5 consists of an elastomer 12 supportedbetween the elastomer members l3 and 14. The upper elastomer supportmember 13 is secured to and supported by the housing 11 of the base mass1 whereas the upper elastomer support ring 14 is secured to thecylindrical housing 15 adjacent to the feeder mounting plate 16 of theframe mass 3.

The feeder mounting plate 16 is provided with a support disc 17 tosupport the feeder bowl 4 which is secured to the mounting plate 16 bythe bolt 18 received in the threaded opening 20 of the feeder bowlmounting plate l6.

The electromagnet 6 is secured to the base mass 1 by the bolt 21 and thenut 22 which supports the field core 23 on the electromagnet base plate24. The base plate 24 is provided with the base guides 25 which arereceived in corresponding apertures in the base mass 1. Spring washer 26is provided between the base mass 1 and base plate 24 to permitadjustment of the height of the field core 23 relative to its armature27 secured, through the armature base plate 28, to the underside of thefeeder bowl mounting plate 16. Upon adjustment of the nut 22 the coilbase plate quides 25 aid in adjustment of the proper air gap 30 betweenthe armature 27 and the field core 23.

As well known in the vibratory art, the electromagnet 6 consists of afield core 23 of E-shape, the central leg of which contains the coilwinding 31 and the three pole faces of the field core 23 provide auniform air gap 30 with the face of the armature 27.

The electromagnet 6 is part of the vibratory exciter means 9 and in thematerial handling device of FIG. 1 and imparts vertical vibratorymovement through the elastic coupling means 5 to the frame mass 3. Theelectromagnet 6 imparts vibratory movement to the two mass vibratorysystem in only one mode of vibration, namely, vibrational forces alongthe vertical axis.

The electromagnets 7 and 8 of the vibratory exciter means 9 have thesame corresponding parts as electromagnet 6. However, the electromagnets7 and 8 comprising the rest of the vibratory exciter means 9 areemployed in a horizontal plane and thus impart vibrations to the twomass vibratory system in a horizontal mode of vibration, the effect ofwhich, in nature, is a torsional component of vibration.

Although other secondary directional modes of vibration may be born insuch an exciter system, in principle, only two orthogonal components ofvibration are set in motion, the compound effect of which produces aresultant excursionary path of displacement on the feeder frame 3. Byindependent control of the exciter means 9, the components of vibrationcan be controlled to variably adjust the operating phase relationbetween the operation of the vertically disposed electromagnet motor 6relative to that of the horizontally disposed electromagnets 7 and 8 andalso change the magnitude of the orthogonal components of vibration topermit variable selection in the degree of eccentricity of theexcursionary path of displacement from that of a straight line to one ofany number of elliptical shapes. The desired excursionary path ofdisplacement to be imposed on the feeder frame is dependent upon thefeeding application involved as well as the weight and size of materialto be fed.

Referring to FIG. 2, the electromagnet motors 7 and 8 are secured to theindented portion 32 of the housing 11 by means of bolt 33 and nut 34.The electromagnets 7 and 8 are identical to the electromagnet 6, eachhaving a coil winding 31 and a field core 23, the latter of which ismounted on the core base plate 35. The base plate 35 is provided withthe guides 36 which are received by the apertures 37 in the indentedportion 32 to permit the uniform adjustment of the air gaps 38, betweenthe pole faces of the cores 23 and their respective annatures 27. Thespring washers 26 are provided between the core base plate 35 andindented portion 32 of the housing 11 in order that the adjustment ofthe air gap 38 may be accomplished through the turning of the nut 4.

It will be noted from FIG. 2 that the armatures 27 are secured to theoutwardly extended arms 40 of the cylindrical housing 15 through themounting or armature base plates 41.

FIG. 3 illustrates a modified embodiment of the material handling deviceof FIG. 1 in that the material handling devices of FIG. 3 employs onlyone elastic coupling means 5. It will be noted that the elastic couplingmeans 5 of FIG. 1 involve concentric elastomers 12 whereas theembodiments in FIG. 3 employ one elastomer ring 42. The structure ofFIG. 1 is the preferred embodiment since the use of concentric elastomerrings 12 provides a more stable two mass vibratory system as compared tothe use of a single elastomer 42 shown in FIG. 3.

The elastomer 42 is supported by the elastomer support ring 13 on thehousing 11 of the base mass 1 as well as being supported from the framemass 3 by the flange member 43. The elastomer ring 42 is supportedbetween the metal rings 44 and 45 which are positioned on the shoulder46 of the elastomer support ring 13 and the shoulder 47 of the flange43. The elastic coupling means 5 as shown in FIG. 3 is clamped inposition by means of the bolt members 48 threaded radially relative tothe central axis of the material handling device through the housing 11against the elastomer support member 13.

The metal ring 45 may consist of aluminum whereas the metal ring 44 mayconsist of steel in order to reduce the massiveness of the frame mass ascompared to the base mass and thus maintain larger rotational inertia inthe base mass as compared to the frame mass.

FIG. 4 is another embodiment of the elastic coupling means 5 of FIG. 1except in FIG. 4 the elastomer ring members 50 and 51 are employed asthe elastic coupling means 5 between the base mass 1 and the frame mass3. The housing 11 of the base mass 1 supports the annular clampingmember 52 which secures the elastomer member 50 between the elastomermounting plate 53 and their armature support member 54 of the frame mass3. By the same token, the elastomer 51 is supported beneath the annulararmature support member 54 on the elastomer mounting plate 55 which issecured to the base mass. Thus upon tightening of the fastening member59 of the annular elastomer support member 52, the elastomer members 50and 51, comprising the elastic coupling means 5, are squeezed orcompressed in position, as shown in FIG. 4. Thus, the compression upontightening support member 52 against the elastic coupling means 5 willdirectly alter and effect the elastic characteristics of the latter toselectively vary the natural frequencies of the two mass system.

An important difference in the elastic coupling means of FIG. 4 ascompared to that shown through FIGS. 1 through 3 should be noted in thetype of node set up in the elastomer. The node is that plane incrosssection of the elastomer where there is no motion in the elastomerfrom zero to maximum shear or compression imparted to the elastomer bythe exciter means 9. In this connection, the elastomer structure shownin FIGS. 1 through 3 involve only shear components to form the node inthe elastomer, whereas in the elastomer structure shown in FIG. 4, twotypes of components are present. In the horizontal or torsional planethere is a shear component whereas in the vertical plane there isimparted to the elastomers 50 and 51 a compression action or component.

Referring now to FIGS. 5 through 8, there is shown a two mass torsionalvibratory system substantially similar to that shown in FIGS. 1 through4 except for the elastic coupling means. The material handling device ofFIG. 5 comprises a base mass 1 which supports an annular housing 11, theinner surface of which employs at periodical intervals, the mountingblocks 56. The base mass 1 supports the E-shaped field core 23 on thecore base plate 24 through the mounting bolts 57. The core base plate 24is provided with the spring washer 58 in order that adjustment to theair gap 30 may be made through the mounting bolts 57. The coil winding31 is supported on the core 23 for electrical excitation. The armature27 is secured to its mounting plate 28 by the mounting bolts 60 to theframe mass 3.

The elastic coupling means 5 consists of disposed sets of parallel leafspring members 61 and 62, the former of which are disposed in thevertical direction and thus permitting a horizontal or torsional mode ofvibration and the latter of which are disposed in a horizontal plane andthus permitting a vertical mode of vibration. The two resilient systemsor leaf spring members 61 and 62 are joined together or rigidlyinterconnected by the mounting block 63. The bolt members 64 clamp theends of the spring members 61 and 62 to the rigid interconnectingmounting block 63. The central or horizontally disposed spring members62 are centrally secured to the frame mass 3 by the bolt member 60 whichalso secures the armature 27 to the frame mass 3. The outer ends of thevertically disposed leaf spring members 61 are secured to the mountingblocks 56. Spacers 65 may be provided to permit flexing of the springmembers in the intended directional modes of vibration.

As shown in FIG. 6 the mounting blocks 56 are secured to the housing 11by the bolt members 66, the latter of which are disposed within theintended portions 67 of the annular housing 11.

It should be noted that the means provided for adjusting the air gap 30between the electromagnets 7 and 8 and their corresponding armatures 27consists of the bolt members 68 threadably secured to the core baseplates 35 which may be simultaneously threaded from the base plate 35while threading inwardly the bolt member 70, which is threadably securedwithin the housing 11 in order to reduce the gap 30 between the armature27 and the corresponding core 23. In order to make the air gaps 30larger, the reverse procedure is done, in that, the bolt members 68 aretightened while simultaneously loosening the adjusting bolt member 70.It can be seen from the air gap adjustment structure of FIG. 6 ascompared to the air gap adjustment of FIG. 2 that the latter employs aspring biased adjustment while the former may require more minipulationin achieving the desired air gap.

The general arrangement of the material handling device of FIG. 7 issimilar to the material handling device of FIGS. 5 and 6 except in thatthe elastic coupling means 5 consist of a spring block member 71 havingtransverse slits 72 to produce a spring member 71 and solid block ends73 and 74 with a central spring section 75 consisting of spring membershaving cross-sectional areas which are substantially square shape inorder to permit flexing of the spring block member 71 not only in ahorizontal or torsional directional mode of vibration but also in avertical directional mode of vibration. The solid block member 73 actsas a mounting block for the spring member 7 l and is secured to thehousing 11 of the base mass 1 whereas the mounting block 74 is securedto the feeder bowl mounting plate 16 of the frame mass 3.

FIG. 8 shows still another modification of the elastic coupling meanswhich consists of the leaf spring members 76 each of which are twistedsubstantially near their ends at 77 to produce a set of verticallydisposed spring sections 78 and a set of horizontally disposed springsections 80 due to the 90 twist imposed on the spring members at thepoints 77. A central opening 81 is provided for receiving the horizontaldisposed spring members 80 to the frame mass 3. The openings 82 areprovided in the ends of the vertical disposed spring members 78 tosecure the same to mounting blocks on the housing 11 of the base mass 1.Such a leaf spring structure eliminates the need of jointure blocks suchas disclosed in FIG. 5 at 63.

The structure of the material handling device of FIGS. 9 and isidentical to that as shown in FIGS. 1 and 2 except for the elasticcoupling means 5. In FIG. 9 the elastic coupling means 5 consists ofwire spring members 83 radially disposed relative to the axial center ofthe frame mass 3 which are secured in the annular clamping members 84and 85 to the base mass 1 and frame mass 3, respectively. The wirespring members 83 are capable of flexing in a horizontal directionalmode of vibration as well as a vertical directional mode of vibration inorder to permit compound vibratory motion on the feeder frame 3.

As noted in FIG. 10, the wire spring members 83 are symmetricallydisposed between the base mass 1 and the frame mass 3 about the verticalaxis of vibration of the material handling device. The spring clampmembers 84 and 85 are provided with spaced semi-circular grooves 86 toreceive the ends of the wire spring members 83 and are sufficientlysmaller in diametrical size than the diameter of the wire spring membersto securely hold wire spring members in position during the vibratoryoperation of the material handling device.

Although only one series of radially disposed and symmetricallypositioned wire spring members 83 may be employed as the elasticcoupling means 5 between the base mass II and the frame mass 2, thepreferred embodiment is to employ concentrically disposed elastic springsystems as illustrated in FIG. 9 in order to obtain a more stablevibrating operation of the two mass vibratory system.

All of the foregoing examples of a versatile two mass swing systemcomprising this invention employ independently controlled vibratoryexciter means and novel elastic coupling means in a two mass torsionalpendulum swing motor system and are generally referred to as bowl orparts feeders. However, the structures employed and methods utilized inthis invention are also applicable in other types of vibratoryequipment.

Referring to FIGS. 11 and 12 there is shown a vibratory feeder forstraight feeding applications employing a vibratory exciter means toimpart to the feeder frame independent horizontal and vertical modes ofmotion through elastic coupling means which permits the independenthorizontal and vertical components of motion to be effective to swingthe feeder frame. The feeder frame 87 represents the feeder mass and issupported on the base mass 88 through the elastic coupling means 5. Thebase mass 88 is supported on the isolaters 90 which are attached to thebrackets 91 which in turn are secured to the inside of the frame 92 ofthe base mass 88.

The base mass 88 also supports the U-shaped bracket 93 which supportsthe vibratory exciter means 9 as in the previous structures of two massvibratory swing systems comprising this invention, the exciter means 9comprises the electromagnets 94 and 95 which consist of the E-shapedfield cores 96 having the pole faces 97. The central leg of the E-shapedfield cores 96 support the coil windings 98. The electromagnets 94 and95 are supported on their respective base plates 100 and, as shown inprior applications, are secured to the frame 93 of the base mass 88 bythe bolt and nut 101. The base plates 100 are provided with the guides102 and the spring washers 103 in order that a variable adjustment ofthe air gap 104 may be accomplished.

The armature bracket 105 is supported from the feeder frame 87 and inturn support the armatures 106 and 107 of the respective electromagnets94 and 95. The armatures 106 and 107 are supported on the armature baseplates 108 which in turn are secured to the armature bracket 105.

Upon excitation of the electromagnet 94, a horizontal component ofvibration is imparted to the armature bracket 105 and feeder frame 87.On excitation of the electromagnet 95, a vertical component of vibrationis imparted to the armature bracket 105 and the feeder frame 87. Throughthe control means employed herein, the operating phase relation andmagnitudes of the components of vibration force as applied to the feederframe 87 may be varied in order to accomplish a change in theexcursionary path of motion imposed upon material being fed forwardalong the bottom of the feeder frame 87 and as a result obtain theoptimum material feed rate for any given feeding application.

The elastic coupling means 5 is similar in function to that shown inFIG. 5 in that it employs horizontally and vertically disposed sets ofparallel leaf springs, the ends of one set being connected to the feederframe 87 and the ends of the other set being connected to the base mass88. As shown in FIG. 12, vertically disposed springs 110 are connectedto the horizontally disposed sets of springs 111 by the U-shaped bracket112. The coupling bracket 112 joins each independent set of leaf springs110 and 111 at their mid-section. The ends of the leaf springs 11 areconnected to the feeder frame 87 through the bracket members 113. Theinside face of the base frame 92 also supports a U-shaped bracket 114 towhich the ends of the vertically disposed leaf springs 110 are securedto by means of the bolts 115.

It will be noted in FIGS. 11 and 12 that two sets of vertically disposedleaf spring systems 110 are employed whereas only one set ofhorizontally disposed leaf springs 111 is employed for supporting thefeeder frame 87.

The straight feeder structure of FIG. 13 may also employ the elasticcoupling means similar to that illustrated in FIGS. 1 through 3 whichemploys the elastomer block members 116 which are supported on the baseframe 92 by the mounting plate 1 17, which is supported on the isolators90, and from the feeder frame 87 by the mounting plate 118. Due to theelasticity of the elastic mounting blocks 116, independently controlledhorizontal and vertical modes of vibration may be imparted to the feederframe 87.

FIG. 14 shows the control circuit diagram for controlling the vibratoryexciter means 9. The vertically disposed electromagnet 6 is connectedacross the supply source L1 and L2. The horizontally disposedelectromagnets '7 and 8 for imparting the horizontal component ofvibration to the feeder frame are connected in parallel and in turnconnected in parallel with electromagnet 6. Connected in series witheach of the electromagnets is a control circuit which is commonlyreferred to as trigger circuit employing a silicon controlled rectifier120 having gate control circuit employing a diode 121 and 122. Thediodes 121 and 122 are connected at their anodes and the cathode of thediode 121 is connected to the gate of rhe SCR 120 whereas the cathode ofthe diode 122 is connected through one line to the resistance 123 whichin turn is connnected to the anode of the SCR 120. Anotherline connectsthe cathode of diode 122 to the variable resistance 124. Both anodes ofthe diodes 121 and 122 and capacitance 125 are connected to the otherside of the variable resistance 124. Capacitance 125 is connected to thecathode of the SCR 120. The variable resistance 124 permits variance inthe voltage applied to the gate of the SCR 120 in order that themagnitude of the pulses supplying the vibratory exciter means may bevaried.

As shown in FIG. 14 the variable impedance 126 is connected in serieswith the vertically disposed electromagnet 6. The adjustment of theimpedance 126 varies the phase relation between the operating currentand applying voltage to the vertically disposed magnet 6 which in turneffects the operating phase relation of the vertically disposedelectromagnet relative to the horizontally disposed electromagnets 7 and8. In varying the impedance 126, it may be necessary also to change thegate voltage applying to the SCR 120 in order to obtain a desiredresultant excursionary path of displacement for feeding materials in thematerial handling device whether it be a straight line of adjustablelength and inclination or an elliptical path of motion of adjustablesize, eccentricity and inclination. Thus, the use of the impedancecontrol 126 effects the magnitude of the applying voltage and,therefore, adjustment may be necessary through the variable resistance124 to correct the applied voltage to the SCR 120. The applied voltageto the vertically disposed electromagnet 6 may be brought back to itsoriginal level in order that the desired feed action applied to thefeeder frame may be obtained or the optimum feeding requirement for agiven feeding application may be achieved.

The amplitude of vibration of the independently controlled horizontaland vertical exciter means may be adjusted by adjusting the resistance124 and also provide, at any instant, correct adjustment of the feedangle of a vibratory feeder to obtain the most effective feeding actionunder the particular feeding conditions encountered.

The adjustment of the impedance 126 effects the phase relation betweenthe current form and voltage form as applied to the electromagnet 6,while the same phase relation of applied current and voltage toelectromagnets 7 and 8 remains constant. Thus the overall result is achange in the operating phase relation of the vertically imposedcomponent of motion as compared to the horizontally imposed component ofmotion to produce different compound vibratory paths of motion of thefeeder frame so that an optimum feed rate may be obtained for a givenfeeding application.

In connection with FIG. 14, this same control circuit may be employedwith the structure shown in FIGS. 1 l, 12 and 13 wherein the verticallydisposed electromagnet 6 of FIG. 4 would be vertically disposedelectromagnet 95 and horizontally disposed electromagnets 7 12 and 8would be replaced by horizontally disposed electromagnet 94.

The double pole-double throw switch 127 may be employed in electricalcontrol circuit of the horizontal exciter means in order to change thedirection of motion of the material moving along the feeder frame. Thereversing of the current applied to the electromagnets 7 and 8 merelychanges the phase relation of these horizontally disposed electromagnetas compared to the vertically disposed electromagnet by 180 so that theresultant compound vibratory motion applied to the feeder frame is at afeed angle of the same magnitude and inclination as the original feedangle but with an inclination in the opposite direction.

It does not matter whether the selection switch 127 is employed in thecircuitry for the horizontally or vertically disposed vibratory excitersince the resultant effect in phase shift is the same.

The supply source for connection with the terminals L1 and L2 in FIG. 14is generally of the alternating type. However, it should be realizedthat in order to achieve the primary object of the invention, that is,to effectively, as well as selectively, change the phase relation of thecurrent through the vertical and horizontal electromagnet coils toproduce the desired path of vibratory motion on the feeder frame. Forexample, one may eliminate the complete SCR control circuit from boththe circuits of horizontal and vertical vibratory exciter means toobtain an alternating current through the vibratory exciter means. Thiswould complete an AC operated two mass vibratory system wherein it wouldbe only necessary to control each of the respective magnitudes in theseparate modes with a shunt control comprising a variableauto-transformer connected in parallel with the electromagnet coils. Ifpulsating DC is employed a variable resistance may be connected inparallel with the respective rectifiers of the vertical and horizontalexciter means. Again, the operating phase relation of the verticalexciter means relative to the horizontal exciter means may be varied byproviding the impedance 126 in series with the vertical vibratoryexciter means.

Another example would be the elimination of only one SCR control circuitfrom one of the circuits of either the horizontal or vertical vibratoryexciter means. The resultant exciting frequency would be a rectifiedcurrent to one of the electromagnet coils of the vibratory exciter meansand an alternating current to the other electromagnet coil of thevibratory exciter means to produce the desired motion. Thus, the SCRamplitude control would be provided for one mode of vibration and an ACshunt control, as previously explained, for the other mode of vibrationwith the impedance 126 for the operating phase control in either thevertical or horizontal mode of vibration.

Referring to FIG. 15, the auto-tranformer 130 takes the place of thecontrol 120 shown in FIG. 14 and their primary section is connectedbetween lines L1 and L2 and their secondary section extends to the endof the winding whether it be straight or circular. The secondary circuitis for the vertical exciter 6 is supplied through the connection 131 tothe anode of the diode 132 the cathod of which is connected by the line133 of the exciter 6 the other end of the exciter is connected by theline 134 to the variable impedance 135. The variable connection 136 ofthe variable impedance is connected directly to the variable connection137 of the secondary of the auto-transformer.

The horizontal exciters 7 and 8 are connected in like manner, the lineL1 is connected to the one end of the auto-transformer 138, however, thesolid state semiconductor diode 140 is connected to the cross points ofthe reversing switch 141 one end of which is connected to the line L1and the other side of which is connected by the line 142 to one side ofeach of the horizontal exciters 7 and 8. The other end of the coils ofthe exciters 7 and 8 are connected by the line 143 to the variableimpedance 144. The variable connection 145 to the variable impedance 144is also connected to the variable connection 146 which defines the endof the secondary of the auto-transformer. The end of the primary of theauto-transformer 138 is connected directly to line L2.

Thus to reverse the direction of operation of the feeder means onemerely reverses the switch 135 in the same manner as that described withrelation to the switch 127 in FIG. 14. Each of these auto-transformersare in fact the amplitude control means as set forth in the followingclaims and they permit one to vary either the vertical or the horizontalcomponents through their respective exciter means 6 for the vertical and7 and 8 for the horizontal components.

From the foregoing it is apparent that the invention herein disclosedinvolves control of the vibratory motion of a two mass swing systemwherein several exciter means may be employed with an elastic couplingmeans capable of flexing in at least more than one direction to producetwo independently controlled harmonic directional modes of vibration.Upon excitation of the exciter means, two independent components ofvibration are imposed in the directional modes of vibration. Flexibility in the control means permits adjustment of the feed rate ofmaterial being fed in the feeder frame.

The change in feed rate may be by individual or simultaneous adjustmentof the vertical and horizontal components of motion and the phaserelation therebetween. Such adjustment to the vibratory components ofmotion produce a change in the resultant path of vibratory motionimposed upon the feeder frame. This resultant path of vibratory motionmay be selected to produce the optimum feed rate for a given feedingapplication, whether an optimum resultant path of motion is of straightline configuration of adjustable length and inclination relative to thetrough or track of the feeder frame or of elliptical path configurationof adjustable size, eccentricity and inclination.

In connection with adjustment of the horizontal and vertical componentsof motion, it should be noted that it is preferable to adjust only thehorizontally disposed exciter means since adjustment of the verticallydisposed exciter means may produce excessive bouncing or vibration. Thusthe vertically disposed exciter means may be held constant at an optimumlevel of acceleration. The resultant effect through this preferredmethod of control is the most efficient feeding action in the adjustabletwo mass vibratory system.

I claim:

1. A tuned two mass swing system including a base serving as a reactionmass and a feeder frame serving as a feeder mass supported from the baseby elastic coupling means permitting independent horizontal and verticalcomponents of vibration to be effective to swing said feeder frame in acontrolled excursionary vibratory path of displacement for feedingmaterials, independent horizontal vibratory exciter means andindependent vertical vibratory exciter means to independently supplysaid horizontal and vertical components of vibration to said feederframe, characterized by control means connected to independently andvariably control said exciter means to independently change themagnitude of each of said horizontal and said vertical components ofvibration and to independently and variably adjust the operating phaserelationship between said horizontal and vertical components ofvibration of said vibratory exciter means to regulate the action of thematerial moved on said feeder frame.

2. The tuned two mass swing system of claim 1 characterized in that saidelastic coupling means consists of symmetrically balanced horizontallyand vertically disposed sets of parallel leaf springs having theadjacent ends of each set rigidly interconnected and the other end ofeach set connected respectively to said feeder frame and to said base.

3. The tuned two mass swing system of claim 2 characterized in that saidhorizontally disposed leaf springs are connected at their opposite endsto the central portion of said feeder frame to provide a linearvibration along a vertical path and the vertically disposed leaf springsare connected at their opposite end to the outer portions of said baseto provide a torsional vibration about a vertical central axis.

4. The tuned two mass swing system of claim 1 characterized in that saidelastic coupling means consists of a spring means disposed radiallyrelative to the axial center of said feeder frame and capable of flexinghorizontally and vertically and secured at one end to said feeder frameand at the other end to said base to produce a torsional vibration abouta vertical central axis and a lineal vibration along a vertical path.

5. The tuned two mass swing system of claim 1 characterized in that saidelastic coupling means consists of an elastomer means secured on oneside to said feeder frame and on the other side to said base. 7

6. The tuned two mass swing system of claim 5 characterized in that saidelastomer means is an annular elastomer ring means about a verticalcentral axis of said feeder frame and capable of flexing torsional andvertical and secured at one side to said feeder frame and at the otherside to said base to produce a torsional vibration about said verticalcentral axis and a lineal vibration along a vertical path.

7. The tuned two mass swing system of claim 5 characterized in that saidelastomer means consists of the plurality of annular elastomers securedin concentric arrangement about a vertical central axis of said feederframe and capable of flexing horizontal and vertical and secured at oneside to said feeder frame and at the other side to said base to producea torsional vibration about said vertical central axis and a linealvibration along a vertical path.

8. The tuned two mass swing system of claim 5 characterized in that saidelastomer means are symmetrically disposed relative to said feeder frameand said base.

9. The tuned two mass swing system of claim 5 characterized byadjustable means to alter the elastic characteristics of said elasticmeans to change the horizontal and vertical natural frequencies of thetwo mass swing system.

10. The tuned two mass swing system of claim 1 characterized in thatsaid control means includes independent switch means to reverse thephase relation of either of said horizontal or vertical components ofmovement relative to other to reverse the direction of resultant feedingmovement imposed on said feeder frame.

1 1. The tuned two mass swing system of claim 1 characterized in thatsaid control means includes amplitude control means to independently andselectively vary the vibratory action of each of said vibratory excitermeans to effect the full range of the relative and obtainable vibratorycomponents of force of said horizontal and vertical vibratory excitermeans alone and together with the combined resultant vibratory forceimposed on said feeder frame.

12. The tuned two mass swing system of claim 1 characterized in thatsaid control means includes magnitude control means to selectively varythe magnitude of each of said vibratory components of force of saidvibratory exciter means, and variable impedance means in said controlmeans connected to selectively adjust the phase relation between saidhorizontal and vertical vibratory forces of said exciter means to effecta full control range of the horizontal and the vertical components offorce and the time sequence of their respective magnitudes to changesaid excursionary path of displacement of said feeder frame and producethe optimum feed rate and action on said feeder frame for a givenmaterial feeding application.

13. A tuned two mass swing system including a base serving as a reactionmass and a feeder frame serving as a feeder mass to which horizontal andvertical components of vibration are imparted thereto, elastic couplingmeans connecting said base and feeder frame to permit vibratorydisplacement of the latter in horizontal and vertical modes of motion topermit horizontal and vertical components of force to be cooperativelyeffective to swing said feeder frame in a controlled excursionaryvibratory path of displacement, horizontal and vertical vibratoryexciter means to independently impart said horizontal and verticalcomponents of force to said feeder means, and control means to variablyadjust the magnitudes of each component independently and the operatingphase relation of said horizontal and vertical components of force ofsaid vibratory exciter means to selectively vary the form of saidexcursionary vibratory path of displacement to control the action of thematerial moved on said feeder frame.

14. In a circuit for independently controlling the horizontal andvertical components of vibration in a tuned two mass swing systemcomprising a vibratory exciter means connected to supply a verticalcomponent of vibration to said two mass swing system and supplied by afree alternating current source, a second exciter means connected inparallel to said vertical vibratory exciter means to supply a horizontalcomponent of vibration to said two mass swing system, an amplitudecontrol means connected in series with each of said horizontal vibratoryexciter means, and variable impedance connected in series with saidvertical vibratory exciter means to variably adjust the operating phaserelation between said vertical and horizontal components of vibrationproduced by said vibratory exciter means.

15. The control circuit of claim 14 characterized by a variableimpedance connected in series with said horizontal vibratory excitermeans.

16. The control circuit of claim 14 characterized in that said amplitudecontrol means is an auto-transformer connected in parallel with each ofsaid vibratory exciter means.

17. The control circuit of claim 14 characterized in that said amplitudecontrol means includes a gate controlled semi-conductor rectifier havingits anode and 16 cathode connected in series with said vibratory excitermeans, and gate controlled circuit connected in parallel with a variableimpedance means.

18. The control circuit of claim 17 characterized in that said amplitudecontrol means is connected in series with only one of said vibratoryexciter means to provide different exciter frequencies to each of saidvibratory exciter means.

19. The control circuit of claim 14 characterized by said switch meansto reverse the connection of said amplitude control means to either ofsaid vibratory exciter means.

20. The control circuit of claim 19 characterized in that said switchmeans is a double pole-double throw switch.

21. The circuit of claim 14 characterized in that said variableimpedance includes a variable resistance in series with a woundelectromagnet coil of said vertical vibratory exciter means.

22. In a vibratory material handling device, the method of independentlyvarying the amplitude of vertical and horizontal components of vibrationwithout effecting the horizontal and vertical natural frequencies of thevibratory material handling device comprising the steps of supportingthe device for independent horizontal and vertical vibratory movement,independently regulating the horizontal and vertical vibratory feedingcomponents of the material handling device to adjust the movement of thespecific material therein, and independently regulating the amplitude ofvibration of the independent horizontal and the independent verticalvibratory components to select the optimum material feed rate andselected action of the material in the device.

23. In a vibratory material handling device, the method of controllingthe path of movement of materials in the device without effecting thehorizontal and vertical natural frequencies of the vibratory materialhandling device comprising the steps of supporting the device forindependent horizontal and vertical vibratory movement, independentlyregulating the horizontal and vertical vibratory feeding components tothe material handling device to adjust the movement of the materialtherein, and independently regulating the phase relation of thehorizontal and vertical vibratory components to change the excursionarypath of motion imposed upon the material in the device.

24. In a vibratory material handling device, the method of varying theoperating phase relation of vertical and horizontal components ofvibration without effecting the horizontal and vertical naturalfrequencies of the device comprising the steps of supporting the devicefor independent horizontal and vertical vibratory movement,independently regulating the horizontal and vertical vibratory feedingcomponents of the material handling device, and regulating the phaserelation of the amplitude of vibration of a selected vibratory componentrelative to the other vibratory component while simultaneouslyregulating the magnitude of one vibratory component relative to theother to obtain the optimum material feed rate and determine the actionon the material in the device for any given feeding application.

25. In a vibratory material handling device, the method of varying thedirection of the path of movement of the material in the devicecomprising the steps of supporting the device for independent horizontaland vertical vibratory movement, providing controlled current impulsesto impart independent regulated horizontal and vertical vibratorycomponents to the device, and changing the phase sequence of the currentimpulses of the selected horizontal and vertical vibratory component tochange the direction of the path of movement and action of the materialin the device.

26. A vibratory electromagnetic drive for imparting torsional and axialvibrations to a working member used to convey materials for vibration,said drive comprising: a base with shock-absorbers; a traverse; a commonintermediate rigid member, resilient means connecting said rigid memberto said base and to said traverse so as to form two resilient systems,one of which is supported by said base, and the other by said traverse,one of said systems including means enabling torsional vibrations andbeing stiff with respect to force applied along the longitudinal axisand yieldable to a torque acting on said axis, the other resilientsystem including means enabling axial vibrations and being stiff withrespect to the torque applied to said longitudinal axis and yieldable toforce directed along said axis; and a pair of electromagneticexciter-means, each being coupled to a respective resilient system toimpart torsional and axial vibrations to a working member connected tosaid traverse.

27. A vibratory electromagnetic drive as claimed in claim 26, whereinsaid electromagnetic exciter means 18 respectively comprises anindividual means for controlling the amplitude of its magnetic flux,thereby providing control over the amplitude of the torsional and axialvibrations respectively.

28. A vibratory eletromagnetic drive as claimed in claim 26, wherein atleast one of the electromagnetic exciter means comprises means forcontrolling the relative phase shift of the magnetic fluxes induced bythe electromagnetic exciter means to control the relative phase shiftbetween the torsional and axial vibrations.

29. A tuned two mass feeder system including a base serving as areaction mass and a feeder serving as a feeder mass supported from saidbase by elastic coupling means permitting independent axial andtorsional components of vibration effective to swing said feeder about arotary central axis for feeding materials, independent axial vibratoryexciter means and independent torsional vibratory exciter means toindependently and respectively supply said axial and said torsionalcompo nents of vibration to said feeder.

30. The two mass feeder system of claim 29 characterized in that saidelastic coupling means consists of rigidly interconnected ends ofindependent axial and torsional resilient springs, the other ends ofsaid independent springs connected respectively to said feeder frame andto said base.

1. A tuned two mass swing system including a base serving as a reactionmass and a feeder frame serving as a feeder mass supported from the baseby elastic coupling means permitting independent horizontal and verticalcomponents of vibration to be effective to swing said feeder frame in acontrolled excursionary vibratory path of displacement for feedingmaterials, independent horizontal vibratory exciter means andindependent vertical vibratory exciter means to independently supplysaid horizontal and vertical components of vibration to said feederframe, characterized by control means connected to independently andvariably control said exciter means to independently change themagnitude of each of said horizontal and said vertical components ofvibration and to independently and variably adjust the operating phaserelationship between said horizontal and vertical components ofvibration of said vibratory exciter Means to regulate the action of thematerial moved on said feeder frame.
 2. The tuned two mass swing systemof claim 1 characterized in that said elastic coupling means consists ofsymmetrically balanced horizontally and vertically disposed sets ofparallel leaf springs having the adjacent ends of each set rigidlyinterconnected and the other end of each set connected respectively tosaid feeder frame and to said base.
 3. The tuned two mass swing systemof claim 2 characterized in that said horizontally disposed leaf springsare connected at their opposite ends to the central portion of saidfeeder frame to provide a linear vibration along a vertical path and thevertically disposed leaf springs are connected at their opposite end tothe outer portions of said base to provide a torsional vibration about avertical central axis.
 4. The tuned two mass swing system of claim 1characterized in that said elastic coupling means consists of a springmeans disposed radially relative to the axial center of said feederframe and capable of flexing horizontally and vertically and secured atone end to said feeder frame and at the other end to said base toproduce a torsional vibration about a vertical central axis and a linealvibration along a vertical path.
 5. The tuned two mass swing system ofclaim 1 characterized in that said elastic coupling means consists of anelastomer means secured on one side to said feeder frame and on theother side to said base.
 6. The tuned two mass swing system of claim 5characterized in that said elastomer means is an annular elastomer ringmeans about a vertical central axis of said feeder frame and capable offlexing torsional and vertical and secured at one side to said feederframe and at the other side to said base to produce a torsionalvibration about said vertical central axis and a lineal vibration alonga vertical path.
 7. The tuned two mass swing system of claim 5characterized in that said elastomer means consists of the plurality ofannular elastomers secured in concentric arrangement about a verticalcentral axis of said feeder frame and capable of flexing horizontal andvertical and secured at one side to said feeder frame and at the otherside to said base to produce a torsional vibration about said verticalcentral axis and a lineal vibration along a vertical path.
 8. The tunedtwo mass swing system of claim 5 characterized in that said elastomermeans are symmetrically disposed relative to said feeder frame and saidbase.
 9. The tuned two mass swing system of claim 5 characterized byadjustable means to alter the elastic characteristics of said elasticmeans to change the horizontal and vertical natural frequencies of thetwo mass swing system.
 10. The tuned two mass swing system of claim 1characterized in that said control means includes independent switchmeans to reverse the phase relation of either of said horizontal orvertical components of movement relative to other to reverse thedirection of resultant feeding movement imposed on said feeder frame.11. The tuned two mass swing system of claim 1 characterized in thatsaid control means includes amplitude control means to independently andselectively vary the vibratory action of each of said vibratory excitermeans to effect the full range of the relative and obtainable vibratorycomponents of force of said horizontal and vertical vibratory excitermeans alone and together with the combined resultant vibratory forceimposed on said feeder frame.
 12. The tuned two mass swing system ofclaim 1 characterized in that said control means includes magnitudecontrol means to selectively vary the magnitude of each of saidvibratory components of force of said vibratory exciter means, andvariable impedance means in said control means connected to selectivelyadjust the phase relation between said horizontal and vertical vibratoryforces of said exciter means to effect a full control range of thehorizontal and the vertical components of force anD the time sequence oftheir respective magnitudes to change said excursionary path ofdisplacement of said feeder frame and produce the optimum feed rate andaction on said feeder frame for a given material feeding application.13. A tuned two mass swing system including a base serving as a reactionmass and a feeder frame serving as a feeder mass to which horizontal andvertical components of vibration are imparted thereto, elastic couplingmeans connecting said base and feeder frame to permit vibratorydisplacement of the latter in horizontal and vertical modes of motion topermit horizontal and vertical components of force to be cooperativelyeffective to swing said feeder frame in a controlled excursionaryvibratory path of displacement, horizontal and vertical vibratoryexciter means to independently impart said horizontal and verticalcomponents of force to said feeder means, and control means to variablyadjust the magnitudes of each component independently and the operatingphase relation of said horizontal and vertical components of force ofsaid vibratory exciter means to selectively vary the form of saidexcursionary vibratory path of displacement to control the action of thematerial moved on said feeder frame.
 14. In a circuit for independentlycontrolling the horizontal and vertical components of vibration in atuned two mass swing system comprising a vibratory exciter meansconnected to supply a vertical component of vibration to said two massswing system and supplied by a free alternating current source, a secondexciter means connected in parallel to said vertical vibratory excitermeans to supply a horizontal component of vibration to said two massswing system, an amplitude control means connected in series with eachof said horizontal vibratory exciter means, and variable impedanceconnected in series with said vertical vibratory exciter means tovariably adjust the operating phase relation between said vertical andhorizontal components of vibration produced by said vibratory excitermeans.
 15. The control circuit of claim 14 characterized by a variableimpedance connected in series with said horizontal vibratory excitermeans.
 16. The control circuit of claim 14 characterized in that saidamplitude control means is an auto-transformer connected in parallelwith each of said vibratory exciter means.
 17. The control circuit ofclaim 14 characterized in that said amplitude control means includes agate controlled semi-conductor rectifier having its anode and cathodeconnected in series with said vibratory exciter means, and gatecontrolled circuit connected in parallel with a variable impedancemeans.
 18. The control circuit of claim 17 characterized in that saidamplitude control means is connected in series with only one of saidvibratory exciter means to provide different exciter frequencies to eachof said vibratory exciter means.
 19. The control circuit of claim 14characterized by said switch means to reverse the connection of saidamplitude control means to either of said vibratory exciter means. 20.The control circuit of claim 19 characterized in that said switch meansis a double pole-double throw switch.
 21. The circuit of claim 14characterized in that said variable impedance includes a variableresistance in series with a wound electromagnet coil of said verticalvibratory exciter means.
 22. In a vibratory material handling device,the method of independently varying the amplitude of vertical andhorizontal components of vibration without effecting the horizontal andvertical natural frequencies of the vibratory material handling devicecomprising the steps of supporting the device for independent horizontaland vertical vibratory movement, independently regulating the horizontaland vertical vibratory feeding components of the material handlingdevice to adjust the movement of the specific material therein, andindependently regulating the amplitude of vibration of the independenthorizontal and the independent vertical vibratory components to selectthe optimum material feed rate and selected action of the material inthe device.
 23. In a vibratory material handling device, the method ofcontrolling the path of movement of materials in the device withouteffecting the horizontal and vertical natural frequencies of thevibratory material handling device comprising the steps of supportingthe device for independent horizontal and vertical vibratory movement,independently regulating the horizontal and vertical vibratory feedingcomponents to the material handling device to adjust the movement of thematerial therein, and independently regulating the phase relation of thehorizontal and vertical vibratory components to change the excursionarypath of motion imposed upon the material in the device.
 24. In avibratory material handling device, the method of varying the operatingphase relation of vertical and horizontal components of vibrationwithout effecting the horizontal and vertical natural frequencies of thedevice comprising the steps of supporting the device for independenthorizontal and vertical vibratory movement, independently regulating thehorizontal and vertical vibratory feeding components of the materialhandling device, and regulating the phase relation of the amplitude ofvibration of a selected vibratory component relative to the othervibratory component while simultaneously regulating the magnitude of onevibratory component relative to the other to obtain the optimum materialfeed rate and determine the action on the material in the device for anygiven feeding application.
 25. In a vibratory material handling device,the method of varying the direction of the path of movement of thematerial in the device comprising the steps of supporting the device forindependent horizontal and vertical vibratory movement, providingcontrolled current impulses to impart independent regulated horizontaland vertical vibratory components to the device, and changing the phasesequence of the current impulses of the selected horizontal and verticalvibratory component to change the direction of the path of movement andaction of the material in the device.
 26. A vibratory electromagneticdrive for imparting torsional and axial vibrations to a working memberused to convey materials for vibration, said drive comprising: a basewith shock-absorbers; a traverse; a common intermediate rigid member,resilient means connecting said rigid member to said base and to saidtraverse so as to form two resilient systems, one of which is supportedby said base, and the other by said traverse, one of said systemsincluding means enabling torsional vibrations and being stiff withrespect to force applied along the longitudinal axis and yieldable to atorque acting on said axis, the other resilient system including meansenabling axial vibrations and being stiff with respect to the torqueapplied to said longitudinal axis and yieldable to force directed alongsaid axis; and a pair of electromagnetic exciter means, each beingcoupled to a respective resilient system to impart torsional and axialvibrations to a working member connected to said traverse.
 27. Avibratory electromagnetic drive as claimed in claim 26, wherein saidelectromagnetic exciter means respectively comprises an individual meansfor controlling the amplitude of its magnetic flux, thereby providingcontrol over the amplitude of the torsional and axial vibrationsrespectively.
 28. A vibratory eletromagnetic drive as claimed in claim26, wherein at least one of the electromagnetic exciter means comprisesmeans for controlling the relative phase shift of the magnetic fluxesinduced by the electromagnetic exciter means to control the relativephase shift between the torsional and axial vibrations.
 29. A tuned twomass feeder system including a base serving as a reaction mass and afeeder serving as a feeder mass supported from said base by elasticcoupling means permitting independent axial and torsional compoNents ofvibration effective to swing said feeder about a rotary central axis forfeeding materials, independent axial vibratory exciter means andindependent torsional vibratory exciter means to independently andrespectively supply said axial and said torsional components ofvibration to said feeder.
 30. The two mass feeder system of claim 29characterized in that said elastic coupling means consists of rigidlyinterconnected ends of independent axial and torsional resilientsprings, the other ends of said independent springs connectedrespectively to said feeder frame and to said base.